Transmission



March 24, 1942. SNEED v I 2,277,157

TRANSMISS ION Filed Dec. 31, 1935 10 Sheets-Sheet 1 3nventor 70H /V S/VEED (Ittomegs J. SNEED TRANSMISSION Marh 24, 1942.

Filed Dec. 51, 1935 10 Sheets-Sheet 2 3nventor 7 JOHN SAM-0 (Ittornegs J. SNEED TRANSMISSION March 24, 1942.

10 Sheets-Sheet 3 Filed Dec. 31, 1955 .TOf/A/ S/VEfID attorney 5 March 24, 1942.

J. SNEED TRANSMIS S ION 1O Sheets-Sheet .4

Filed Dec. 31, 1935 JOB/V S/VffD fi T 17) attbimegs March 24, 1942.

J. SNEED TRANSMISSION Filed Deg. 31;; 1935 10 Sheets-Sheet 5 Zinnentor March 24, 1942. Y J. SNEED 2,277,157

TRANSMISSION Filed Dec. 51, 1955 10 Sheets-Sheet 6 3nnentor Jab/IV SAIL-0 r (Ittomegs M rch 24, 1942. .J. SNEED 2,277,157

TRANSMISSION Filed Dec. 51, 1955 10 Sheets-Sheet? Z'snoentor JOH/V S/VEfD March 24, 1942. J. SNEE D TRANSMISSION 10 Sheets-Sheet 8 Filed Dec. 31, 1935 3iwentor Y 7 70/1/11 SNEED (Ittbrneg 5,

J. SNEED TRANSMISSION March 24; 1942.

Filed Dec. 51, 1955 10 Sheets-Sheet 9 JOHN SAM-ED (Itfornegs March 24, 1942. J. SNEED 2,277,157

TRANSMISSION Fild Dec. 31, 1935 10 Sheets-Sheet 1O uni-lull! .57 15kg e/a' r" 60 g am Gttomegs Patented Mar. 24, 1942 UNITE STATES 20 Claims.

This invention relates to transmission mechanism and more particularly to transmission mechanism of the automatic type which brings about and retains such speed ratios between the driving and driven members as are most appropriate to meet the demands imposed upon the instrumentalities with which it is operated under the varying conditions of such operation.

For the purpose of illustrating and describing my invention I will refer to it in the environment of an automobile of the type in common use today, but I expect those skilled in the art to appreciate that the application of the principles of my transmission or the transmission itself may well be suited to many other and varied uses.

Certain novel features herein contained may be regarded as constituting improvements upon the subject matter disclosed in my copending applica ion Serial No. 749,795 filed October 24, 1934. Part of the subject matter herein contained is common to that of my prior application, and to that extent this application is a continuation of my said prior application.

Certain of the broader objects of my invention are similar to those set forth in my prior application and may be briefly summarized as fol- I lows i It is among the broader objects of my invention to provide an automatic transmission which will select and establish gear ratios between the driving and driven shafts most appropriate to the speed and load conditions existing between said shafts; to provide an automatic transmission particularly adapted for an automobile which will automatically correlate the engine speed to 5 the vehicle speed in a manner conducive to optimum performance for all conditions of speed and load; toprovide an automobile transmission capable of reflecting in its change and maintenance of gear ratios the conditions most effective to carry out the demands of the driver of the vehicle, and which is subject to the driver's control through its response to such demands; and to provide a transmission capable of carrying out these and other objects which is compact, economical of manufacture, relatively saving of" weight and space, and efficient and fool-proof in operation.

Other objects having more particularly to do with improvements upon and inventive advances beyond the subject matter of 'my prior applica-/ tion include the provision of a novel method of over-drive control conducive to better economy and smoother vehicle operation under. all conditions where maximum performance is not desired, but which provides maximum performance in any gear ratio should the same at any time be demanded: Other objects are to provide a novel over-drive mechanism and control thereall the advantages of the automatic speed changes of the transmission are available in reverse as well as in forward speeds; and to provide a system of gearing and control capable of furnishing an over-drive under one condition and a reverse drive or neutral" under other selectable conditions. Other objects are to provide an improved overrunning clutch and to provide an advantageous release and control therefor; to provide a system of gearing in which bearing and tooth loads are materially reduced and in which a more perfect balance of the moving parts is obtained; tov provide improved'mecha nism for selecting, engaging, disengaging and maintaining the various gear reductions or relationships; and to provide an i lubrication.

Other objects having more especially to do with the improvements upon the subject matter of my copending application are to provide a transmission capable of giving satisfactory performance and results with widely different kinds of friction materials having different coeflicients of friction either in the first instance or as the material may wear or change its characteristics during the life of its operation; to provide a transmission which will give uniform satisfactory performance throughout a long range of wear and change of dimension, particularly of the friction material which may become worn in its operation; to provide an equal distribution of the tooth'loads throughout the gears of the planetary trains in the transmission and smooth and noiseless operation thereof; to provide for gear ratios throughout the long life of the wearing parts in spite of the wear of such parts; to

provide a" no back brake and means for releas- 55 ing andcontrolling the same; to provide particfor; to provide a reverse drive by virtue of which mproved system ofthe distribution of and reduction in bearing loads i had to the accompanying drawings.

ularly against damage or injury to the gear teeth as between the gears that I prefer to be manually shifted, as for example in changing from forward to reverse drive; and to provide interlocking or interconnecting controls, particularly in connection with the means for effecting a reverse drive to insure a smooth correlation between the transactions necessary or desirable to effect a satisfactory shift from forward to reverse drive and vice versa.

Other objects of my invention are to provide a transmission in which the relative speeds of the mover are established andmaintained throughout the range of their operation. Other objects of my invention include the provision of a transmission in which changes of speed relationships between the driving and driven members is effected smoothly and positively and without sub- I stantial loss of torque or driving impulse from the driving to the driven member, and in which the forces which act to create or maintain one or another speed relationship between the driving and driven members are commensurate with the load being transmitted.

Other objects and advantages; will appear from the following description of preferred forms .of

embodiments of my invention, reference being The essential characteristics are summarized in the claims. i s

In the drawings Figure 1 is a longitudinal section of my transmission as assembled for usein an automotive vehicle and includes a part of a universal joint at the rear end and in dotted lines indicates the-crank-shaft of the prime mover and a clutch mechanism at the forward end; Figure 1A is an enlarged view of a portion of the torque drum and cover employed in the transmission.

Figure 2 is a transverse section taken along the line 2-2 of Figure 1 and illustrates an overrunning clutch mechanism;

Figure 2A is an enlarged view of the teeth of the clutch of Figure 2;

Figure 3 is a transverse section taken along the line 3-3 of Figure 1 and illustrates the mounting of a governor weight assembly;

Figure 4 is a transverse section taken along the line 4-4 of Figure 1 and illustrates a second speed planetary gear assembly;

Figure 5 is a transverse section taken along the line 5-5 of Figure 1 and illustrates the low speed planetary gear assembly;

Figure 6 is a transverse section on the line 6-8 of Figure 1 and illustrates a'mechanism hereafter referred to as the low' speed gear starter;

Figure '7 is a transverse section looking forwardly of the transmission on line |1 of Figure 1 and illustrates a driving connection between the torque and load responsive parts of the transmission and an over-drive mechanism;

Figure 8 is a transverse'section looking rearwardly on line 8-8 of Figure 1 and illustrates theplanetary gear arrangement of the overdrive; a

Figure 9 is a transverse section on line 9-4 of Figure 1 and illustrates the yoke shifting mechstarter;

Figure 11 is a longitudinal section of a modifled form of my invention wherein the over-drive mechanism of the preferred embodiment is omitted;.

Figure 12 is a transverse section looking forwardly on the line l2-l2 of Figure 11 illustrating the overrunning clutch and manual control therefor;

Figure 13 is a transverse sectional view on line I3il of Figure 11 illustrating the governor weight assembly in this form of my invention;

Figure 14 is a transverse sectional view looking forwardly on line l4l4 of Figure 11 illustrating the second speed planetary gear assembly and the transmission brake employed to effect a reverse drive;

Figure 15 is a transverse sectional view on line lS-l! of Figure 11 illustrating the low speed gear assembly;

Figure 16 is a transverse sectional view on line lB-IS of Figure 11 illustrating a splined connection between a driven drum torque gear member concentric thereto;

Figure 17 is a transverse sectional view looking rearwardly on line l'|l'l of Figure 11 showing the yoke and shifting means employed in connection with reverse drive;

Figure 18 is a transverse sectional view of a modified form of reverse control for the transmission shown in Figure 11;

Figure 19 is an elevation of the control shown in Figure 18;

Figure 20 is a diagrammatic'showing of the cam and governor weight rollers employed in the preferred form of my transmission;

Flgure'21 is a transverse sectional view of the vacuum actuated over-drive control mechanism;

Figure 22 is a transverse sectional view of the valve employed in the mechanism of Figure 21;

Figure 23 is a fragmentary diagrammatic illustration of a latch mechanism that may be embodied in the over-drive control.

Referring to the drawings the transmission generally identified at T is contained within a bell housingv I suitably flanged at its forward end and secured to a motor unit generally identified at M. The crankshaft S of the motor unit is' secured to the forward face of the flywheel F which carries an automatic clutch 0 preferably constructed according to my co-pending application, Serial No. 18,811, filed April 29, 1935.

The forward end of the transmission bell hous- Q reverse mechanism OD. The rear wall of the I splined to the hub portion of the clutch mechanism C. At the rearward end of the transmission the driven member I00, which may incidentally form a part of a universal joint, not wholly shown, is rotatably mounted in the antifriction bearing I21 and is splined to a driven ring gear 0 of the over-drive mechanism, Between the driving shaft I0 and the driven shaft I00 are interposed the change speed, over-drive and reverse mechanisms.

Turning now more particularly to the change speed mechanism, the driven shaft I00 above referred to is hollow at its forward 'end and supports within its hollow end, through sleeve hearing I40, the rearward end or tail shaft-of the gear carrier 30. The gear carrier extends forwardly from its mounting in the shaft I00 and is shaped and proportioned to embrace or surround the driving shaft I0 and functions generally to support planetary gears which intermesh with sun gears on the driving shaft and surrounding clutch gears selectably engageable with the driven shaft, see also Figs. 4 and 5.

More specifically the gear carrier extends forwardly from the bearing I through a sleeve bearing I30 and is provided with a flanged part or radially extending plate 33 which may be referred to as the back plate of the gear carrier inasmuch as similar plates spaced therefrom comprise complementary parts of the gear carrier structure. A central plate 32 of the gear carrier unit has formed thereon three circumferentially spaced rearwardly extending spacing blocks 34a, see Fig. 5. The spacing blocks. 34a are internally threaded to receive cap screws 34b extending through apertures in the rear plate 33 of the gear carrier. Forwardly extending spacing blocks 34 (see Fig. 4) are provided on the forward face of the central gear carrier plate 32 and are engaged by similar cap screws arranged in the forward gear carrier plate 3|. The forward end of the gear carrier unit 30 comprises the plate 3I having a forwardly extending sleeve surrounding and rotatably mounted upon the driving shaft I0 through the sleeve bearing I23. Thus the three carrier plates 3|, 32 and 33 as connected through the spacing blocks 34 and 34a form a unitary structure rotatably mounted with respect to the driving shaft I0 and the driven shaft I00.

Between the forward plate 3I and the central plate 32 of the gear carrier is mounted a series of planetary gears I! and Ho, see Fig. 4. These planetary gears, which may be referred to as the second speed gears, are mounted in pairs substantially 120 apart and are arranged so that the inner gears I! are in mesh with the sun gear II integrally formed with the driving shaft, and.

the outer gears IIa are mounted a greater distance from the center of the driving shaft and mesh with gears II andalso mesh with the toothed parts I3 of a second speed-clutch ring gear. The arrangement of gears I! and I'll: to

transmit rotation from the sun gear II to the surround'ng clutch-gear is such that the same directional rotation will be maintained and the bearing pin pressure of the gears I1 and Na will be reduced so that needle or quill bearings I3I may be employed to support the planet gears.

Bearing pins 23 and 23a employed to support the planet gears I1 and IIa respectively on the gear carrier are mounted in suitable recesses provided in the opposing faces of gear carrier plates 3| and 32.

A planetary gear assembly similar to the sec-- ond speed gear assembly above described is employed in connection with thelow speed drive. As illustrated in Figure 5 the inner planet gears I8 of the planet gear couple I8-I8a are in mesh with sun gear I2 integrally formed with the driv-- ing shaft I0 and are also in mesh with planets Ida which transmit the rotation to the toothed parts I5 of the low speed clutch ring gear. The planetary gears of the low speed assembly are arranged in pairs as shown and advantageously within the gear carrier 30 and in mesh with the inner planet gears I1 and I8 mounted on said gear carrier. Suitable end thrust bearings E, see Fig. 1, preferably comprising bronze disks or washers, are interposed between the ends of each of the planets and the adjacent faces of the carrier plates 3|, 32 and 33 adjacent the supporting pins 23, 23a, 24 and 24a.

,It will be observed particularly in Figures 4 and 5 that the disposition of the planets in three symmetrically arranged pairs in the low and second speed gear trains respectively provides an even distribution of weight and provides a symmetrical distributionof torque loads and tooth pressures in each system. The distribution of forces resulting from tooth pressures is such that there is no tendency to displace either the sun gears or the ring gears laterally relative to each other, whereby the bearing loads due to driving pressures in both the sun and the ring gears are substantially negligible. Since the bearing loads imposed on the planet bearings are all absorbed within the gear carrier system including the plates 3i, 32, 33, no external forces result totend to displace the carrier relative to the main bear ings at the rear and forward ends of the transmission.

I prefer that the several disks l3 and I3 which compositely comprise the ring gears for each of the planetary trains be mounted without external radial support since there is no resulting tendency for radial displacement thereof arising by .virtue of any driving load and since such a mounting insures that each disk will properly center itself with'respect to the three planets with which it meshes. It will be appreciated that when driving load is transmitted or is begun to be transmitted from the planets to the tooth ring gear disks I3 and/or IS, the tooth reactions at the 'three points of contact will tend equally to force the disks radially outwardly at each of the three points (the three points being preferably re-- spectively apart), and thereby not only tends to center each of the. disks with respect to 7 the three planets with which it is engaged, but

also tend to shift, if need be, and center the disks so that each of the planets delivers an equal portion of the driving loadinto each of metric symmetry with respect to the planets, I

but also into a position to take equal loads from each of the three planets. This arrangement insures not only quiet operation of the gears, but also long life and the absence of excessive tooth pressures at one point with respect to any of the others.

In the conventional planetary system wherein the drive from the sun gear is through a single set of planetary gears to a ring gear, it will be observed that the bearing pin pressure of each of the planets is substantially twice the tooth pressure on the planet. In a planetary system constructed according to my invention the drive from the sun gear through the inner series of planets in mesh therewith is not across the diameter (180) of the planet as in the conventional system, but is through an angle of about ably comprises the following novel arrangement.

An annular ring I5 U-shaped in cross section,

90. The drive from the inner series of planets to the outer series and to the ring gear is likewise through an angle of about 90'. This arrangement effects a reduction in planet pin bearing pressure that is a function of the angle of the drive through the planets and thus my construction is well suited to the use of needle bearings or other anti-friction bearings that would not be suited to the conventional single series planet system.

It will be appreciated from examination, particularly of Figure 1, that my transmission adapts itself to the use of helical gears in the planetary system. The end thrust resulting in the inner series of planets by the drive from the sun gear is transmitted to the. earcarrier.

inner drum 8 which is provided with thrust bearings I 30 and I39 at the ends thereof, where it engages the gear carrier. The gear carrier itself is fitted with end thrust bearings 34 and I35 on radial faces of the driving shaft, and thus the end thrusts effected by the drive through the transmission are opposed.

From the foregoing description those skilled in the art will understand that when, by means yet to be described, the drive is effected through the driving shaft Ill, the gear I! thereon, the planetary gears l8 and l8a, a reduction in speed will be effected between the driving shaft l0 and the low speed clutch gear engaging the planetary gears lBa. When, however, the drive is from driving shaft l0 through the gear ll, planatery gears i1l'|a and the clutch gear in engagement therewith, a lesser reduction is effected between the driving shaft and the driven clutch gear. It will further be understood by those skilled in the art at this point in the description of the invention that, when by means presently to be described, no relative rotation is permitted between the driving shaft l0 and either the' low speed orsecond speed planetary gear systems that a direct drive may be established between the driving shaft in and the driven parts of the transmission.

To restrain the gear carrier 30 from negative I rotation and maintain the low speed and second speed planetary gears in position to transmit rotation from the sun gears to the clutch gears when rotation of the driven shaft is desired, I provide an overrunning clutch at the forward end of the gear carrier, which prefersee Fig. l, is secured to the forward extremity of the gear carrier and pivotally supports on pins 18 a series of spaced eccentrically weighted pawls Ii, see also Fig. 2. An annular two-part ring "I, secured to the forward cover plate 4 of the transmission housing, is notched as at 82 to receive the noses of the pawls 16 carried by the ring 15. 'Springs I! urge the noses of the pawls'into the notches 12 of the fixed ring 80. When the ring I5 is rotated in a counterclockwise direction as viewed in Figure 2, the pawls overrun the notches in the ring by reason of the inclined engagement between the back faces 11 of the pawls with the complementary facing of the notches. Whenever the carrier speed rotates the ring 15 rapidly enough the weighted portion H of the pawls swing outwardly against the springs 19' and draw the noses of the pawls away from the notches in the ring 80. Conversely as the carrier slows down the noses of the pawls are urged radially outward into the notches and ator about zero relative speed between the rings I5 and 80 so engage the notches as to prevent relative clockwise rotation of the carrier with respect to the ring as viewed in Figure2. It thus follows that there may b short periods when the carrier ring 15 is overrunning the fixed ring at relatively low speeds when the pawls will intermittently engage the notches and cause an upleasant sound. To deaden the sound I prefer that the ring 80 be formed in two disk-like halves between which is preferably secured a ring of sound deadening material 8| such as fabric impregnated with phenol resin compounds. The fabric ring 8| is notched as shown in Figure 2A so that it has overhanging portions 82 which pro- Ject into the notches on one side thereof to engage the backsides I! of the noses of the pawls, and cushion the contact of those surfaces during the limited periods of time above mentioned.

The foregoing description has been premised on the assumption that means are provided for selectively transmitting the torque from the low speed and second speed clutch ring gear disks l3 and I5 respectively when they are actuated from the driving shaft l0 and sun gears i2-ll integral therewith. The following description is directed more particularly to the means by which the torque and drive are selectively taken from these gears to efiect low, second speed and direct drive relationships between the driving shaft l0 and the driven shaft I00.

Rotatably mounted concentrically of the axes of the driving and driven shafts and rotatably supported with respect to the main casing I are two cup-shaped parts or drums 2 and 3 which encompass the gear carrier 30 and its associated parts. Both of the drums are preferably adapted to be formed by deep drawing operations and can be economically manufactured for that reason. Both drums are mounted with respect to each other to rotate substantially in unison and to have a longitudinal sliding fit with respect to each other so that there may be axial movement between them.

The outer drum 2, which may be hereafter referred to as the torque drum, is enlarged at its forward end and is enclosed adjacent its periphery by a centrally apertured cover plate 6 which is mounted thereon for limited axial movement with respect thereto and which extends inwardly but terminates short of the flange or collar Goof the cover 4 of the main housing and is free at all times of said collar. As illustrated in Figure 1A the bolts employed to secure the cover to the flange 2b of the drum 2 are provided withuwashers on the cover plate side and a series of leaf springs 5a are arranged with their free notched ends beneath the said washers. The convex portion of spring leaf bears against the cover plate 5 and the springs thus urge the cover plate into engagement with the flange 2b to compensate for certain clutch and governor weight reactions to be more fully described hereinafter. The rearward end of the torque drum 2 extends inwardly as at 5 and carries thereon, preferably througha spring mounting, a splined torque disk 40. see Fig. 7. The splines 2i of the member 40 are inclined with respect to the longitudinal axis of the transmission and slidably engage the teeth 22 of a helical torque gear member 28. The hub portion of the torque gear extends rearwardly and transmits the torque to the overdrive and reverse mechanism identified generally at OD and thence to the driven shaft I09.

The mounting of the torque disk A0 is effected by positioning the disk .40 between the inner radial wall 6 of the drum 2 and a spaced disk 44 parallel to and rigidly secured to said wall. The torque disk 40 is notched at its outer periphery as at 63 to encompass the pins 25 which secure the disk 44 to the drum 8 and is provided with spaced rectangular apertures intermediate the notches 43 to receive springs 4|. Spring pins 42 extend axially of the springs 4| and are sup- 40. As will be observed from Figure 1 the springs 4| are proportioned to extend laterally on each I side of the rectangular apertures in thedisk Eli and said extended segments abut against similarly formed rectangular apertures in the wall 6 of the torque drum 2 and in the retaining disk 44 carried thereby. The effect of the above described mounting is to cushion torque reactions transmitted from the drum 2 to the torque gear 20 and likewise from the torque gear 20 back to the torque drum 2.

The inner drum 3, see Fig. 1, is provided at; its forward end with a fixed cover plate I- having a forwardly extending annular bearing portion 1a which bears on its inner surface against a sleeve bearing I arranged about the outer end of the forward part of the gear carrier 30. The, combined thickness of the cover I and flange 3b is preferably less than the total longitudinal: travel of the outer drum with respect to the inner drum so as to effect an oil scraping action on the bearing surfaces therebetween and prevent the formation of any sticky deposits which might adversely affect the smooth sliding fit. The. bearing I30 is flanged-as best shown in Figure 1 and will take end thrust imposed thereon from the central portion of the cover plate 1. The rear wall of the inner drum 3 is centrally apertured ported at each end of said apertures in the disk addition to mounting the torque disk and securing the plate 44 also extend axially forward and project through a complementary series of apertures provided in the rear radial wall 8 of r the inner drum 3. The forward portions of the pins 25 have a close sliding fit in the apertures drum 2, thence through the helical spline 2l-22 to the torque gear 20 and thence'to the driven shaft I00.

At the forward end of the inner drum 3 and preferably at the periphery of the flanged rim thereof as at 69 a free close sliding fit is established with theinner surface of the outer drum 2. Thus by the sliding fit established through the pins 25 and the apertures therefor at the rear of the inner drum and through the annular sliding contact at 59 at the forward end thereof. the drums 2 and '8 are maintained in coaxial alignment while the outer drum 2 is longitudinally movable with respect to the inner drum. A group of coil springs it supported between a radial shouldered portion of the inner drum 3 and a plurality of struck in tongues ll formed in the outer drum '2 resiliently urge the outer I drum rearwardly with respect to the inner drum.

Thus when any torque is transmitted through the helical spline 2l22, that is, between the torque gear 20 and the drums 2 and 3 there re-- sults an axially operative component of force which tends to effect relative longitudinal motion between the outer drum 2 and the inner drum'3.

' transmitted through the helical spline 2 |-22 and as will more fully appear, the resultant tendency to move the torque drum 2 fore or aft with respect to the drum 3 is employed according to the precepts of my invention to contribut to the operation of the mechanism, particularly in the selection and maintenance of the various gear ratios orreductions. It will be further noted that the torque gear 20 is rotatably mounted upon the sleeve IS in a manner which permits such circumferential motion relative thereto as may be necessary to affect all the necessary axial movement of the drum 2 with respect to the torque gear or member 20 along the helical splines 2l-22.

The inner drum 3 which has at its forward portion a greater diameter to accommodate the second speed gear assembly than the diameter -at its rear portion, provided to accommodate the low speed assembly. is internally splined axially throughout both of said portions. The splines are preferably formed by depressed ribs 30 as shown in Fig. 1 and rather diagrammatically in Figs. 4 and 5. The splines may be economically formed during the initial drawing operation forming the drum.

A plurality of disks I6 preferably formed of material or composition providing suitable friction surfaces are splined at their outer periphcries and arranged in splined engagement with the rear end of the inner drum 3. The series of disks l5 provided with internal gear teeth at their inner peripheries are arranged alternately be.

tween the friction disks l6 and this assembly of toothed disks and splined disks may be hereafter referred to as the low speed clutch-gear or flexible ring gear in that ro'tation imparted to the disks I may be transmitted to the disks l6 and through the splines thereon to the drum 3 upon with the toothed'disks l3 to transmit torque from the planets ll-l'la and sun gear II to the drum 3. The material forming the splined disks I4 and I8 is preferably a material which will have suitable frictional characteristics under the conditions existing within the transmission shown cumferentially slotted at spaced intervals 38a, see Fig. 6, to receive and support pawl members 38. The rearmost of the group of toothed driving disks ii of the low speed clutch-gear is provided with a series of circumferentially spaced apertures 39, see Fig. 10, which cooperate with the noses of the pawls 38 to permit a pawl and ratchet engagement between the starter ring 35- and said disk. The rearmost friction disk It is interposed between the said apertured driving disk and the starter ring 35. Said friction disk is not splined to the drum 3 but is securely rivets d to the ring 35 and is slotted as at 16a to accom- -modate the pawls 38, see Fig. 10. From the and I have found that an asbestos fabric imgear assembly at the rearward portion of the drum 3, the disks ii are proportioned to mesh with the three outermost gears I80 of the low speed planetary gear system supported by the gear carrier 30. In the absence of any pressure 4 applied to the stack of driving and driven disks l5-l8 rotation of the planetary gears upon their axes may merely turn the driving disks I 5 with respect to the driven disks I6. When through means presently to be described axial pressure is applied to the low speed clutch-gear assembly, it

-will be understood that the drive through the drlvingshaft H), the low speed sun gear l2,

planetary gears l8l8a will transmit the torque through the low speed clutch-gear to the drum 3, through pins to the torque drum 2, through the torque gear 20 and the over-drive mechanism to the driven shaft lilll. Similarly, when axial pressure is applied to the second speed clutchgear assembly, and when pressure is released from the first speed clutch-gear, the driv will be through the drivingshaft ID to the second speed sun gear ll thereon, through the second speed planetary gears l1 and Ho, thence through the second speed clutch-gear to the inner drum 3 and as in the first instance to the driven member I00.

It will further be seen that when pressure is applied to effect a frictional drive through both the low speed and second speed clutch-gear assemblies at the same time, the planetary gears will cease to turn upon their own axes, the gear carrier will turn in the same direction as the driving member and the inner and outer drums and the gear carrier and the entire mechanism carried thereby will rotate as a unit with the driving shaft l8 and a direct drive will be established through the torque gear 20 and through the over-drive to the driven shaft I08. When the last described condition exists the transmispawl and ratchet connection above described it will be observed that normal positive rotation through the driving shaft l8, sun gear l2, planets l8 and l8a and ring gear disks I5 including the rearrnost apertured disk l5 will through the pawl and ratchet tend to rotate the starter ring in the same direction as the said apertured disk.

The starter ring 35 is provided with a series of rearwardly stamped out cams 38 which cooperate with a similarly shaped series of cams 31 pressed forwardly out of the rear wall 8 of the inner drum 3. Rotation imparted to the gear starter through the pawl and ratchet 38-38 is effective through the cam reaction 86-41 to urge the entire starter ring forwardly toward the low speed clutch-gear disk assembly and compress said stack of disks against the radially extending abutment plate 23 secured to the|inner drum 3.

The plate 23 as shown in Figure 1 extends radially inward at about the mid-section of the drum and is secured to the radially shouldered most of the toothed drivingring gear disks l5 the forwardmost of the friction disks it, which planets l8a, particularly when the whole assent-- bly of disks l5 and I6 is compressed in active driving position. Driving torque from the forwardmost of the disks I5 is thus in part transmitted through the said forwardmost friction sion per se is in the normal direct drive or that disk l8 to the plate 23 and thence to the drum 3.

Flat leaf springs 38b secured to the rear face of the gear starter ring 35 preferably by rivets as shown urge the pawls 38 into the apertures 38 of the driving disk. It will be observed, however, that when the drum 3 is rotated at a greater speed than the apertured driving disk that the cam reaction 36-31 will permit the starter ring to move back from a compressing position to an inactive position as shown in Figure 10, and that the starter ring 35 and pawls 38 will override the driving disk having the apertures 33. By virtue of the cam faces on the noses of. the pawls 38 the pawls will be moved out of the apertures and the starter ring will be free to rotate with respect to the driving ring. The springs 38b, however, constantly urge the pawls forward about their forked pivotal connections 380 with the starter ring 35 and whenever the speed of rotation of the drum approaches equality to or tends to drop below the rotational speed of the driving disks in the low speed gear assembly the pawls are urged forwardLv into the notches 38 and the drum is thereupon rotated in the manner shown by the driving disks of the low speed clutch-gear assembly. i y

Between the forward end plate I of the inner drum 3 and the forward end plate of the torque drum 2 and arranged to rotate with drum 3 is a centrifugal governor, see also Fig. 3, which comprises a group of governor weights 50 arranged circumferentially about and formed to abut in their innermost idle position the inturned flange 1a of the inner drum cover plate 1. As shown in Figure 3 the governor weights 50 each define sectors which abut each other laterally in their innermost positions. Eachl of the governor weights 50 is grooved radially on the rear wall thereof as at 53, and is slotted coextensively with said groove in its outer Wall as at 53a to accommodate cams 55 radially mounted in radial slots 55 in the front wall I of the inner drum. The governor weights 50 are each cut away adjacent the inner edge of their forward faces to accommodate a series of retractor springs 52 extending from one governor weight to the other, which tend to hold the governor weights at their innermost position. Each of the governor weights is provided with a rectangular aperture arranged transversely ,of its radial groove 53 and a pair of rollers 5| are supported for free rotation in each of said transverse apertures. ,In each weight the rollers 5| are proportioned to have a greater longitudinal displacement than the thickness of the weight at the bottom of the groove 53, so that the rear roller projects into the groove 53 and is adapted to engage cam faces 60and 5| of the cam 55. The forward roller 5| is normally substantially flush with the forward radial wall of the governor weight, but is adapted to project slightly beyond the forward face of the weight and bear against the smooth rear face of the cover plate 5 of the torque drum 2.

In response to rotation of the drums 2 and 3 the weights 50 will tend to move outwardly in response to centrifugal force against the restraint of retractor springs 52 and against the resistance of the cams 55 to outward movement of the rollers 5| thereover. The effect of this outward movement of the rollers 5| bearing on the cams 55 is to urge the drum 2 longitudinally forward and to urge the cams 55 rearwardly about their pivotal bearings 51 in the forward wall I of the inner drum 3. The earns 55 are free in the slots 55 to move rearwardly through the cover plate I and bear through arcuate notches against the annular rib 58 in the second speed starter ring 54, but are restrained from forward tilting in said aperture by flanges 59,

see Fig. 3, which project laterally of the rear faces of the cams and bear against the inner rearward face of the plate I adjacent the apertures 56. Rearward movement of the second speed starter ring .54, which is interposed between the cams 55 and the second speed clutchgear disks l3 and I4 efieots a compression of the disk assembly against the radially extending abutment plate 29 to transmit torque from the planet gears ||-|'|a to the drum 3.

The movement of the cams 55 as affected by the outward movement of the governor weights above described is also affected by the reaction in the helical spline 2|22, which when the driving torque is positive tends to move the outer drum 2 rearwardly with respect to the inner drum 3.

When a high torque is being transmitted through the helical spline 2|--22 a higher centrifugal force, that is higher speed, must be developed in the governor weights 50 to effect an outward travel of the rollers 5| over cams 55. On the other hand, whenthe torque transmitted through the helical spline 2l-22 is small or negative only a relatively small centrifugal force need be developed by the governor weights to effect an extreme outward movement of the rollers 5| over cams 55.

rollers 5| over the cams 55, it is to be observed that axial force transmitted through the forward rollers 5| to the vwall 5 of the outer drum 2 is always equal and opposite to the reaction of the rollers upon the cams 55. Thus the axial pres sure on the second speed clutch-gear disks is a function of the torque transmitted through the helical spline 2|--2Z. On the other hand, the torque reaction tending to move or hold the drum 2 rearwardly will not of itself efiect a movement of the cams 55 unless the rollers 5| are drawn outwardly or maintained outwardly by the governor on the operative portions of the inclined surfaces of the cams 55.

. When the rollers 5| are moved outwardly over the cams 55 beyond the point of their pivotal support 51 on the cover plate 1, and thereby permit the squeeze in the rollers 5| to be effective to move the cams and compress the disks of the second speed clutch ring gear |3|4. Thi compressive movement causes the toothed disks |3 to frictionally engage the splined friction disks l4, and tends to bring the disks l4 and the drum 3 up to the higher rotational speed of the disks l3,

and thereby cause the drum to rotate more raptween the operating cam surfaces 50 and 6|, it

will be appreciated (1) that the angle of the cam surfaces 50 and 6| .will have been reduced with respect to the radial plane, and (2) that further outward radial movement of the rollers 5|, particularly over the cam faces 5|, will mainly tend to draw the drum 2 forwardly with respect to the drum 3 rather than to move the. earns 55 rearwardly with respect to the drum 3 or itscover plate I.

When, as above indicated, the drum 2 is moved forwardly with respect to the drum 3 by radially outward movement of the rollers 5| induced by the governor weights 50 over the inclined cam surfaces 6|, the pins 25 engage the low speed gear starter ring 35 and move it bodily forward, and thereby compress the low speed clutch ring gear assembly |5|6, and thereby tend to reduce and eliminate relative movement between the toothed and splined disks of this assembly. Theeffect of engaging the low speed clutch ring gear |5| 6 while the second speed clutch ring gear |3|4 is held in engagement is to reduce all relatively internal movement in both planetary systems, bring the carrier 30 up to the speed of the driving shaft and rotate the drums 2 and 3 at the speed of the driving shaft.

To insure a release of the low speed clutchgear prior to engagement of the second speed clutch-gear the'splines of the friction disks l6 In connection with the radial movement of the governor weights 50 and of the low speed clutch-gear are proportioned to have a slight movement with respect to grooves in the drum 3. See Fig. 5. The slight amount of initial overrunning movement of the drum 3 induced by the second speed engagement thus permits the drum carried cam 31 to have a substantial movement with respect to cam 36 of the starter ring 35. Since the engaging pressure between the friction disks l6 and the driving disks i5 is relieved by this preliminary cam movement the low-speed clutch-gear is fully released and cannot drag after the second speed clutch-gear causes the said overrunning movement.

It will be observed that the foremost friction disk I6 is unsplined and functions to temper the releasing action above described in its frictional engagement with the plate 29 of the drum on its forward face, and against the foremost toothed disk IS on its rear face. Thus a part of the engagement between the friction disks and the toothed disks tends to be continued to the extent of the drive through said unsplined friction disk. Among the advantages that result from the provision of the unsplined disk above described is that any tendency of the low speed clutoh-gear to chatter by reason of the lost motion in the splines is obviated. Although the frictional drive maintained by the foremost unsplined disk is a relatively small part of the total drive, I have found it to be suiiicient to prevent a chatter of the low speed clutch occasioned by unevenness in torque load while in low gear, and to contribute to a smooth release of low-gear as second speed gear is engaged.

As heretofore stated, axially extending pins 25 the cam and roller reaction which would tend to are carried by the rear radial wall of the outer drum 2 and protrude through the rear radial wall of the inner drum i-adjacent to the low speed starter ring 35, see particularly the lower portion of Fig. 1. When the second speed drive has been exclusively established the first speed starter ring 35 has assumed its rearmost position, as shown in Fig. 1, and theforward ends of the pins 25 are proximate thereto, but preferably spaced therefrom perhaps a little less than shown in Fig. 1, albeit the absolute spacing of the pins from the ring at this point may vary within reasonably wide limits to allow for wear of the friction surfaces and other parts. Preferably the forward ends of the pins' 25 extend far enough into the zone of the cam ring 35 to be positioned in the path of the heels of cams 36 to prevent rotation of ring 35 when the splined disks I5 are overrunning the disks 16 by the engagement of the second speed clutch.

Since the position of the governor weights in their outward travel is governed by rotational speed and torque and since their position determines the engagement of second speed and the establishment of direct drive, it will be understood that normal wear in the clutch-gear disks might in the absence of a wear compensating means, vary the conditions required to effect second speed or direct drive. I conceive thatthe thickness, for example, of the splined fric ion disks H and I 6 determines the longitudinal position of the rollers 5| with respect to the-drum 2. The resilient mounting of the cover plate 5' through springs to provides a mounting which compensates for the wear or differences in thickness in the clutch-gear disks and permits the governor weights to bottom against the circumforce the cover 5 from the drum. The resilient mounting of the cover 8 thus provides that the wearing of the friction materials will not change substantially the conditions of speed and load designed to effect the establishment of second speed and direct drive, It will also be observed that since the torque reactions are transmitted through the cover 5 to the clutch-gears that torque shocks are transmitted through the springs in and that said springs thus function to measure and cushion th torque effect upon the clutch gears.

It is to be observed that the low speed clutchgear is thus adapted to be actuated through the pawl, ratchet and cam gear starter, of ring 35 and also to be actuated at a different time by the longitudinal movement of the outer drum 2 resulting from helical spline and centrifugal governor reactions. The first of said low speed clutch-gear actuations is to establish low gear alone and the second of said actuations is to establish a direct drive between the driving shaft l0 and the torque gear 20.

Referring back to the earns 55, the governors 50, and the rollers 5| carried thereby, as shown particularly in Fig. 20, it will be observed that I prefer to form the cams each with an inner operating face 60 and an outer operating face 6|, both inclined to a radial plane of the transmission when the cam is idle. The face 80 is provided with an inactive or idle face 60a and the face 6| has a resistance face Sla.

To enable those skilled in the art to put my invention into practice more readily I will give the values of the governor weights and the inclinacam angles which I have found to be successfully operativein a current model of motor vehicle weighing approximately 2600 lbs., with a motor developing 150 foot lbs. torque at 2300 R. P. M. and about brake horse power at 3750 R. P. M. The combined mass of the governor weights totaled about 5% lbs. and a helical spline inclination at about 36 satisfactorily effected the various gear shifts. The inactive face 601: being inclined about 6 to the radial plane and Joining the inner operating face which is inclined at about 12 to the radial plane. The first operating face Joins the resistance face Ola which is inclined at about 51 to the radial plane and the second operating face 6| which is inclined at about 36 to said radial plane. In connection with the above specific values given for the angle of the cam faces, it is pointed out that said angles are but one of the many factors which are selectively variable. The 'coeflicient of friction between the engaging surfaces in the clutch gears was about .1 to'.15. With the above specific values, I have obtained satisfactory operation of the transmission with a wide range of friction materials, although my present preference is for a material similar to'that heretofore described. In this transmission the low speed-gear ratio was 2.92 to 1 and the second speed gear ratio was 1.61 to 1.

From the foregoing example of specific values for cam angles and the like, which have been i given-to more fully illustrate a specific-operative structure built in accordance with, the precepts of my invegiion, it will be understood that some or all of the values given may be varied within reasonably wide limits without departing from the teaching of this specification, and that the values given above are given for the purpose of illustration and example.

When low gear has been established by the transmission of positive torque through the low speed starter above. described, and the drums 2 and 3 are rotated as the vehicle is moved, the surfaces 60 which at that time are inclined in about the manner shown in Fig. 1 and the reaction through the helical spline 20-2l is transmitted to the rollers through the cover plate 5 of the torque drum and thereby through the in-- clination of the cam faces 60 tending to hold the rollers inwardly in about the position shown in Fig. 1. Under this condition the axial squeeze in the rollers is applied to the cams inside of their respective points of pivotal support 51 on the cover plate I of the inner drum 3, whereby no tendency results from the squeeze to move the cams rearwardly with relation to the said cover plate I. When, however, the effect of the torque squeeze" is overcome by the centrifugal force of the governor weights, the weights and rollers then moveoutwardly on the cam surfaces 60, and all other things being equal, it will be appreciated that'once the governor ward, even though that tendency is modified as the rollers progress in their outward travel.

The foregoing description of a shift from first to second speeds has been premised upon the assumption that the engine throttle has remained substantially constant throughout the shift. In

- such a circumstance the kinetic energy available through slowing down the engine may preferably be dissipated in part through slippage of the second speed clutch and may in part be used to maintain a continuous driving effort or even a controlled acceleration of the vehicle during the have reached the resistance face Bla, while the weights have begun their outward movement a condition has been created under which they would normally tend to continue that outward movement against the same or substantially the same opposition. It will also be appreciated that other conditions do not remain the same,

and that one of the essential changes of the conditions is that the second speed clutch-gear l3-l4 is begun to be engaged with the result that the engine speed tends to be reduced, and that the kinetic energy available through the decreasing engine speed tends to add to.the acceleration of or accelerate the vehicle, and that the latter tendency may measure an increase in torque through the helical spline which tends to increase the squeeze of the rollers 5|.

To more fully provide against the continuance of an undesirable balance of forces which might unduly protract the slippage of the second speed clutch when engagement thereof is desired, 1

preferably provide that outward movement of the rollers 5| over the cam faces 60 be accompanied by an increasing mechanical advantage which reaches a ratio of one to one when the rollers are opposite the rib 58 on the ring 54, and which is preferably a little greaterwhen the rollers reach the junction of the cam faces 60 and Bio as shown in Fig. 20. It will also be observed that by reason of the pivotal support of the cams 55, not only do the rollers have an increasing mechanical advantage in their outward movement over the cam faces 60, but also the rearward tipping of the cams reduces the effective angle of opposition to outward movement of the rollers. 1 provide, however, that the angle of the cam faces cam faces iii and Gla have assumed lesserangles with respect to the radial plane, they still present a greater angle to the rollers than does the face 80, whereby for a time at least under a condition of constant throttle opening and road loads effective to cause the shift from first to second, the. rollers will tend to pause at the face of the resistance angle Gla until such a new increase in speed is established as to urge the rollers further outwardly over the newly presented inclined surfaces of the cam faces Bio. The cam faces 61a are relatively short in extent and are intended primarily to offer a greater resistance to outward movement of the rollers 5| than are the operating faces 6|. Thus when the governor has developed enough centrifugal force to start the rollers over the hump of the resistance face Sla, it will tend to insure continued movement of the rollers over the cam faces 6|,

which then present a lesser angle of resistance,

when direct drive is thus established, the rollers .5l are then bearing on the outermost portions of the cam faces Ill, and at a still higher mechanical advantage with respect to the rib 58 on the ring 56 to more fully insure the maintenance of engagement of the second speed clutch gear l3 l l during direct drive. As mentioned above the resilient support of the cover plate 5 of the 80 be such that when the cams have tipped by compression of the second speed clutch-gear a. maximum amount, there still remain a substantial angle between the cam faces 60 and the radial plane, so that a too rapid or grabbing engagement of the second speed clutch is prevented by reason of-the ever present tendency of the torque reaction to squeeze therollers radially intorque drum 2 permits the governor weights to bottom radially against th cylindrical wall of the drum 2, whilst the squeeze in the rollers is maintained through the springs 5a holding the cover plate rearwardly.

While the foregoing has been premised on the assumption that a substantially constant driving effort has been imposed on the drivingshaft anda substantially constant resistance developed by the driven shaft or at least the torque gear 20 of the transmission, as for example by driving on a smooth level road with the throttle held at a fixed opening while the shifts above described occurred, at least two other points are worthy of note in this connection namely the effect of change in transmitted load in the course of the period comprehended by the shifts, and the wardly as well as upwardly. 7

With respect to changing the: load in the period comprehended by the shifts, it will be appreciated that if just prior to a shift from first to second the throttle is partially closed so that the driving effort is in part reduced, the rollers will move outwardly more readily and more rapidly, and that the positive engagement of second speed may be' very rapidly accomplished and maintained if the driving efiort is not too rapidly reimposed on the system. For that matter,-it will be understood that if the speed is suflicient just prior to the shift out of the low speed ratio, then a reduction in driving effort as by closing the throttle may readily accomplish a shift from low speed into direct drive by reason of the extreme outward movement of the rollers and the compression of both the first and second speed clutches which will be maintained if the driving effort is not too rapidly re-applied to the system.

As to the ability'of the device to shift down from a higher speed, the advantages referred to above which facilitate the shifts upward are equally available to facilitate the shifts downward." For example, when the second speed clutch gear is exclusively engaged an increase in torque load or a decrease. in speed or a combination of those conditions sufficient to initiate an inward movement of the rollers 5| along the cam surfaces 60 will, by reason of the decreasing mechanical advantage of the rollers with respect to the cams 55, increasingly facilitate the inward movement of the rollersand the release of the second speed clutch-gear, and prevent a hanging on of the second speed clutch-gear when the speed and load conditionsdemand a rapid shift to low to most advantageously meet the newly imposed conditions of higher torque and lesser speedh As least as between the torque gear and the driving shaft l0, driving conditions may well arise when negative torque loads are imposed upon the transmission, i. e. when the torque gear 20 tends to drive the driving shaft [0. a condition arises when the transmission has established direct drive, as above described, the

reaction through the helical spline 2l22 will urge the drum 2 forwardly with respect to the drum 3, forcing the pins forwardly and compressing the low speed clutch-gear, and tending to relieve the squeeze in the rollers 5|. So long, however, as the vehicle speed maintains the governor weights 50 in their outermost radial positions as is normal in high or direct drive, then the squeeze in the rollers will be maintained essentially by the governor weights, since the cover plate 5 of the drum 2 is limited in its forward movement with respect to the cover plate I of the drum'3 by reason of the pins 25 comprising the first speed clutch and by the compression of the springs5a. Since the rollers 5| are acting on the outer ends of the cams 55, and at a great mechanical advantage with respect to the second speed clutch-gear, directdrive can very conveniently be maintained while such negative torque is imposed until the vehicle reaches a very low forward speed. When, however, a very low forward speed is reached, which those skilled in the art will appreciate can be determined by the masses of the governor weights, the inclination of the cams, the strength of the springs 10 and 5a, and the like, then the second speed clutch gear may be released which If such 2,277,157 ability of the device to change speeds down-- will result in efiective disengagement of the driving shaft ID from the torque gear 20 through the overrunning of the carrier with respect to the housing as permitted by the one-way clutch 15--80. Of course, if the speed should tend to .increase after the release of the second speed place while the drum 2 was moving forwardly and forcing engagement of the low speed clutch through the pins 25.

At least while transmitting positive torque from the driving shaft It] to the torque gear 20 during the shift from one speed relationship to another, the forces acting to compress the respective clutch gears are controlled to be not substantially incommensurate with the torque to be transmitted. During the initial compression of the first speed clutch gear-to initiate the low speed drive, the compressive forces arise from the cam reaction 35-41 as the starter ring 35 is rotated by the force of rotation of the driving load. The driving load being tempered by the master clutch C, because this is the period of its initial ngagement, whether automatically in response to speed and transmitted torque, as I prefer and have described. in my copendingapplication Serial No. 18,811, or manually or otherwise.- In the engagement of the second speed clutch gear it will be appreciated from the foregoing description that the compression of the disks thereof is measured by the squeeze in rollers 5|, and although the squeezing effect is modified somewhat during the outward travel of the rollers over the pivoted cams 55, still the compression of the plates is not remote from the value of the transmitted torque as reflected through the helical spline 2 l-22. When the low speed clutch is compressed to effect a direct drive, the source ofactuating force primarily comes from the governor weights 50 in opposition to the tendency of the torque reaction to draw the drum 2 rearwardly, but because of this reaction the governor weights are only able to accomplish their outward travel and compress the low speed disks when their force has become one not incommensurate with the transmitted torque.

The foregoing paragraphs have been directed to the parts of the transmission in which speed I changes are effected in response to changes in torque load and rotational speeds in the transmission and the over-drive has been referred to merely as a means to transmit the torque from said torque. and speed responsive parts to the driven shaft N10. The over-drive arranged within the case 9 identified generally at OD is so arranged that when the speed and torque conditions permit, it may be actuated to change the speed ratio between the torque gear 20 and the driven shaft and rotate the driven shaft I00 at a higher speed than said torque gear member. Thus for instance whenthe speed and torque responsive parts of the mechanism have established what has been referred to as a direct drive from the driving shaft III to the torque gear 20, the over-drive may be actuated to rotate the driven shaft I 00 at a higher rotational speed than 

